EP0269647B1 - Palier a glissement radial hydrodynamique - Google Patents

Palier a glissement radial hydrodynamique Download PDF

Info

Publication number
EP0269647B1
EP0269647B1 EP87902409A EP87902409A EP0269647B1 EP 0269647 B1 EP0269647 B1 EP 0269647B1 EP 87902409 A EP87902409 A EP 87902409A EP 87902409 A EP87902409 A EP 87902409A EP 0269647 B1 EP0269647 B1 EP 0269647B1
Authority
EP
European Patent Office
Prior art keywords
tilting
segments
segment
sliding bearing
shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP87902409A
Other languages
German (de)
English (en)
Other versions
EP0269647A1 (fr
Inventor
Paul Gerling
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Braunschweiger Huettenwerk GmbH
Original Assignee
Braunschweiger Huettenwerk GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Braunschweiger Huettenwerk GmbH filed Critical Braunschweiger Huettenwerk GmbH
Priority to AT87902409T priority Critical patent/ATE56507T1/de
Publication of EP0269647A1 publication Critical patent/EP0269647A1/fr
Application granted granted Critical
Publication of EP0269647B1 publication Critical patent/EP0269647B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/03—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/1045—Details of supply of the liquid to the bearing

Definitions

  • the invention relates generically to a hydrodynamic radial plain bearing, - with bearing housing, cylindrical tilting segment receptacle, inserted into the tilting segment receptacle, tilt segments distributed over its circumference and lubricant supply device with lubricant supply openings in the tilting segment receptacle, the tilting segments on the shaft side having a sliding surface with lubricant supply direction transverse to the shaft Edge of their sliding surface and on the back have a tilting shape, the radial section of which corresponds to the cutout of a circle with a radius that is reduced compared to the radius of the cylindrical tilting segment receptacle, wherein the tilting segments on both sides of the tilting shape form a gap with respect to the cylindrical tilting segment receptacle, which according to the tilting shape, ie in a radially outward projection, as it were, under the tilt formation, can extend over the entire width of the individual tilt segments or can be arranged only in regions, for example in the central region of the width of the
  • Such a radial slide bearing must on the one hand master the shaft dynamics or the dynamics of a rotor connected to the shaft and on the other hand work with little loss.
  • the wave dynamics include the vibration amplitudes of the shaft and / or the rotor which are associated with the bending vibration or the critical speeds. It is important to dampen these vibrations.
  • the losses result from the lubricant friction not only in the sliding gaps that form the sliding surfaces of the tilting segments with the surface of the shaft, but also in the spaces between the tilting segments.
  • the gaps on the segment back are wedge-shaped over their entire length in the manner described.
  • the lubricant supply channels run more or less radially in the tilting segments and are located in the area of the segment support. From there, the lubricant is fed to the lubrication gaps.
  • lubricant escapes through the gap spaces, which lubricant hardly contributes to damping the vibrations described at the beginning.
  • the damping takes place practically exclusively in the lubricant layer and is in need of improvement in the case of generic radial plain bearings.
  • the lubricant gets into the space between the tilting segments and, due to turbulence and the resulting internal friction, contributes considerably to power loss and oil loss.
  • the invention has for its object to further develop a generic radial slide bearing so that without additional components, a very pronounced damping of the vibrations described takes place and the oil losses and power loss are reduced.
  • the invention teaches that the gap spaces of the tilting segments have an extension, namely a damping gap area, at least on the wedge-shaped areas formed by the tilting shape opposite the running direction of the shaft, which on the one hand has a surface area of the cylindrical tilting segment receptacle and on the other hand a concentric back surface area of the tilting segment is formed, and that the lubricant supply device has a segment channel which leads obliquely from the lubricant supply transverse groove to the tilting shape and to the associated lubricant supply opening arranged there in the tilting segment receptacle.
  • the invention is based on the knowledge that the gap spaces under the tilting segments can make a significant contribution to reducing oil losses and power loss as well as to damping vibrations if they have areas that are not wedge-shaped, but are designed as damping gap areas with a small gap thickness. This is achieved if damping gap areas are formed, which are formed on the one hand by a surface area of the cylindrical tilting segment receptacle, on the other hand by a concentric back surface area of the tilting segment that is not tilted, and if care is taken to ensure that this damping gap area is also sufficiently long.
  • the lubricant supply device has the described, inclined segment channels, so that no lubricant can penetrate into the tilting segment spaces.
  • the thickness of the damping gap areas and their length must be adapted to the special conditions, taking into account the degree of freedom of tilting of the tilting segments.
  • the thickness of the damping gap regions will be made as small as possible, on the other hand the damping gap regions will extend in the circumferential direction as long as possible.
  • a preferred and proven embodiment of the invention with damping gap regions arranged on both sides of the wedge-shaped regions formed by the tilting segment shape is characterized in that the damping gap region opposite the direction of travel of the shaft is several times longer than the region lying in the running direction, because this region is to a greater extent than the area lying in the running direction can contribute to damping the described vibrations.
  • the damping gap areas in the case of untilted tilting segments, are designed as parallel gaps and have a gap thickness of a maximum of 2%, preferably less than 1 %, of the sliding surface radius of the tilting segments.
  • the invention recommends that the segment channel have a slot-shaped cross section that extends across the width of the tilting segments and that they run into a plurality of lubricant outlet bores that open into the lubricant supply transverse groove, and that the lubricant supply opening is adapted to the cross section of the segment channel.
  • the tilting segments are subjected to considerable mechanical loads. This also includes bending moments with a bending moment axis that coincides more or less with the radial slide bearing axis.
  • a preferred embodiment of the invention is of independent importance (in combination with the other features discussed above) that the tilt formation and the tilt segment are each formed as a single component.
  • the tilting segments constructed in this way have a very large section modulus in relation to the mechanical loads to be absorbed and consequently also a corresponding bending stiffness.
  • the tilting formation can also be formed in a manner known per se on a special component which is inserted into a corresponding receptacle in the back of the tilting segments.
  • the end face of the bearing housing is open, so that the lubricant can flow away as usual.
  • the requirement for good tilting mobility of the tilting segments on the one hand and for a small gap height in the region of the oil transfer from the bearing housing to the tilting segments is met.
  • the basic structure of the hydrodynamic radial slide bearing shown in FIGS. 1 to 3 consists of a bearing housing 1, a cylindrical tilting segment receptacle 2, a plurality of tilting segments 3 inserted into the tilting segment receptacle 2, distributed over their circumference, and a lubricant supply device 4.
  • the tilting segments 3 have, on the shaft side, as usual, a sliding surface 5 with a lubricant supply transverse groove 6 on the edge 7 of the sliding surface 5 opposite the running direction of the shaft and on the rear side a tilting shape 8.
  • the lubricant supply transverse grooves 6 are each provided with a lubricant supply opening 9 assigned.
  • the radial section of the tilting formation 8 corresponds to the section of a circle with a radius r that is reduced compared to the radius R of the cylindrical tilting segment receptacle 2. For this purpose, reference is also made to FIG. 4.
  • This design leads to the tilting segments 3 forming a gap 10, 11 on both sides of the tilting formation 8 relative to the cylindrical tilting segment receptacle 2, which becomes wedge-shaped narrower in accordance with the tilting formation 8, that is to say in an outward radial projection under the tilting formation 8. 1 and 4, it can be seen that the gap spaces 10, 11 of the tilting segments 3 have an extension, namely a damping gap area 10, at least in the wedge-shaped area opposite the running direction of the shaft and formed by the tilting shape 8.
  • This damping gap area 10 is formed, on the one hand, by a surface area of the cylindrical tilting segment receptacle 2, and, on the other hand, by a concentric back surface area 12 of the tilting segment 3, which is considered to be untilted.
  • the arrangement is such that it has a segment channel 13 by means of the lubricant supply device 4, which is inclined from the lubricant supply transverse groove 6 obliquely to the tilting formation 8 and to an arranged lubricant supply opening 9 leads in the cylindrical tilting element holder 2.
  • the damping gap area 10 opposite to the running direction of the shaft is several times longer than the area 11 lying in the running direction. It is understood that the damping gap areas 10, 11 in the figures are exaggerated for illustration reasons. In practice, the arrangement is generally such that the damping gap regions 10, 11, when the tilting segments 3 are not tilted, have a maximum gap thickness D which is approximately 2% of the sliding surface radius GR of the tilt segments 3.
  • the supply of oil is ensured in the radial slide bearing described in that the segment channel 13 has a slot-shaped cross section extending over the width of the tilting segments 3 and runs out into a plurality of lubricant outlet bores 14.
  • the lubricant outlet bores 14 open into the lubricant supply transverse groove 6. It goes without saying that the lubricant supply opening 9 is adapted to the cross section of the segment channel 13.
  • the tilting segments 3 have a very large section modulus. In this respect, they are designed to be very rigid. This is achieved in that the tilting formations 8 and the tilting segment 3 each represent a single component.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

Le palier décrit comporte un logement (1) de palier, un logement (2) cylindrique renfermant des segments basculants (3) répartis à sa périphérie, et un système d'amenée (4) de lubrifiant. Les segments basculants (3) présentent côté arbre une surface de glissement (5) avec une gorge transversale (6) d'amenée de lubrifiant, au niveau du bord de ladite surface de glissement opposé au sens de rotation de l'arbre, et côté envers, une protubérance de basculement (8) dont la coupe radiale correspond au secteur d'un cercle de rayon réduit par rapport au rayon du logement cylindrique des segments basculants. En outre, ces derniers forment des deux côtés de la protubérance de basculement (8) et par rapport audit logement cylindrique (2) un intervalle (10, 11) qui se rétrécit de manière cunéiforme en proportion de ladite protubérance de basculement (8). Ces intervalles (10, 11) possèdent, au moins au niveau de la région cunéiforme opposée au sens de rotation de l'arbre et formée par la protubérance de basculement (8), une région d'intervalle d'amortissement, laquelle est formée d'une part par une région de surface du logement cylindrique (2) des segments basculants, et d'autre part par une région de surface envers (12), qui lui est concentrique, du segment basculant (3). Le système d'amenée (4) de lubrifiant comporte un canal segmenté (13) partant de la gorge transversale d'amenée (6) de lubrifiant, en biais par rapport à la protubérance de basculement (8), et aboutissant dans une ouverture d'amenée (9) de lubrifiant disposée dans le logement cylindrique (2) des segments basculants.

Claims (5)

1. Palier hydrodynamique à glissement radial, comprenant
un carter (1),
un logement cylindrique (2) à segments basculants, des segments basculants (3) intégrés dans le logement (2), et répartis sur le pourtour de celui-ci, et un dispositif (4) d'alimentation en fluide lubrifiant qui comporte, dans le logement (2) des segments basculants, des orifices (9) d'admission de fluide lubrifiant,
les segments basculants (3) comprenant, côté arbre, une surface de glissement (5) avec une rainure transversale (6) d'admission de fluide lubrifiant sur le bord de leur surface de glissement (5) qui fait face au sens de rotation de l'arbre et, côté postérieur, une protubérance de basculement (8) dont la coupe radiale correspond au fragment d'une circonférence présentant un rayon réduit par rapport au rayon du logement cylindrique (2) des segments basculants, les segments basculants (3) formant en outre de part et d'autre de la protubérance de basculement (8), par rapport au logement cylindrique (2), un interstice (10, 11) à rétrécissement cunéiforme en fonction de la protubérance de basculement (8), caractérisé par le fait que les interstices (10,11 ) des segments basculants (3) présentent, au moins dans la région cunéiforme tournée à l'opposé du sens de rotation de l'arbre, et formée par la protubérance de basculement, un prolongement, c'est-à-dire une zone interstitielle d'amortissement (10)
qui est formée, d'une part, par une région superficielle du logement cylindrique (2) des segments basculants et, d'autre part, par une région superficielle postérieure (12) du segment basculant (3), concentrique à la région précitée;
et par le fait que le dispositif (4) d'alimentation en fluide lubrifiant comporte un canal segmentaire (13) qui s'étend à l'oblique, à partir de la rainure transversale (6) d'admission de fluide lubrifiant, jusqu'à la protubérance de basculement (8) et jusqu'à l'orifice associé (9) d'admission de fluide lubrifiant, pratiqué dans le logement (2) des segments basculants et situé dans cette zone.
2. Palier à glissement radial selon la revendication 1, comportant des zones interstitielles d'amortissement disposées de part et d'autre des régions cunéiformes, formées par la protubérance de basculement, caractérisé par le fait que la zone interstitielle d'amortissement (10), tournée à l'opposé du sens de rotation de l'arbre, est plusieurs fois plus longue que la zone interstitielle d'amortissement (11) située dans le sens de rotation.
3. Palier à glissement radial selon l'une des revendications 1 ou 2, caractérisé par le fait que les zones interstitielles d'amortissement (10, 11) sont réalisées sous la forme d'interstices parallèles, et présentent une épaisseur d'interstice (D) qui représente au maximum 2 %, de préférence moins de 1 % du rayon (GR) de la surface de glissement des segments basculants (3).
4. Palier à glissement radial selon l'une des revendications 1 à 3, caractérisé par le fait que le canal segmentaire (13) présente une section transversale en forme de fente, s'étendant sur la largeur des segments basculants (3), et s'achève par de multiples perçages (14) de sortie du fluide lubrifiant, qui débouchent dans la rainure transversale (6) d'admission de fluide lubrifiant; et par le fait que l'orifice (9) d'admission de fluide lubrifiant est adapté à la section transversale du canal segmentaire (13).
5. Palier à glissement radial selon l'une des revendications 1 à 4, caractérisé par le fait que les protubérances de basculement (8) et le segment basculant (3) sont réalisés sous la forme d'une pièce constitutive unitaire.
EP87902409A 1986-05-23 1987-04-28 Palier a glissement radial hydrodynamique Expired - Lifetime EP0269647B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87902409T ATE56507T1 (de) 1986-05-23 1987-04-28 Hydrodynamisches radialgleitlager.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3617289 1986-05-23
DE19863617289 DE3617289A1 (de) 1986-05-23 1986-05-23 Hydrodynamisches radialgleitlager

Publications (2)

Publication Number Publication Date
EP0269647A1 EP0269647A1 (fr) 1988-06-08
EP0269647B1 true EP0269647B1 (fr) 1990-09-12

Family

ID=6301421

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87902409A Expired - Lifetime EP0269647B1 (fr) 1986-05-23 1987-04-28 Palier a glissement radial hydrodynamique

Country Status (5)

Country Link
US (1) US4815865A (fr)
EP (1) EP0269647B1 (fr)
BR (1) BR8707312A (fr)
DE (2) DE3617289A1 (fr)
WO (1) WO1987007341A1 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5288153A (en) * 1993-01-04 1994-02-22 Delaware Capital Formation, Inc. Tilting pad journal bearing using directed lubrication
GB9400392D0 (en) * 1994-01-11 1994-03-09 Chester Keith I Improved bearing assembly
US5720558A (en) * 1995-10-16 1998-02-24 Dresser-Rand Company Tilting bearing pad with an axial feed groove having an exit side profiled area
US5759011A (en) * 1996-05-14 1998-06-02 Dresser-Rand Company Journal bearing assembly
EP1890045A1 (fr) * 2006-08-16 2008-02-20 Siemens Aktiengesellschaft paliers radiaux hydrodynamiques pour gros turbogénérateurs
US7780424B2 (en) * 2008-10-21 2010-08-24 Baker Hughes Incorporated Self leveling dynamically stable radial bearing
US8342821B2 (en) 2010-10-21 2013-01-01 Baker Hughes Incorporated Tuned bearing
US20140205224A1 (en) * 2011-09-29 2014-07-24 Hitachi, Ltd. Direct Lubrication Tilting Pad Journal Bearing
DE102013223329A1 (de) * 2013-11-15 2015-05-21 Bosch Mahle Turbo Systems Gmbh & Co. Kg Gasdynamisches Luftlager
TWI597436B (zh) * 2016-03-15 2017-09-01 財團法人工業技術研究院 液靜壓軸承
CN109312778B (zh) * 2016-05-26 2020-12-01 弗兰德-格拉芬斯达登有限公司 具有注射器和偏转器的流体动力轴承
WO2018029835A1 (fr) * 2016-08-10 2018-02-15 三菱日立パワーシステムズ株式会社 Ensemble palier et machine tournante
DE102020209611A1 (de) * 2020-07-30 2022-02-03 Siemens Energy Global GmbH & Co. KG Hydrodynamisches Radial-Kippsegmentlager

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3023055A (en) * 1960-03-14 1962-02-27 Earl A Thompson Pressure fed rocker shoe bearing
FR1450715A (fr) * 1964-08-19 1966-06-24 Escher Wyss Sa Palier d'arbre avec rotor glissant sur des patins segmentaires orientables
US3351394A (en) * 1965-01-07 1967-11-07 Mechanical Tech Inc Hydrostatic bearings for a rotatable element
FR1492819A (fr) * 1965-12-28 1967-08-25 Productions Ind Et De Distrib Coussinet à coins d'huile auto-adaptés ou analogue et ses diverses applications
CH430344A (de) * 1965-12-31 1967-02-15 Bbc Brown Boveri & Cie Radialgleitlager
US3589782A (en) * 1969-09-18 1971-06-29 Westinghouse Electric Corp Damper bearing to increase rotor stability
CH569895A5 (fr) * 1973-12-19 1975-11-28 Maag Zahnraeder & Maschinen Ag
DE3414910A1 (de) * 1984-04-19 1985-10-24 A. Friedr. Flender Gmbh & Co Kg, 4290 Bocholt Kippsegment - gleitlager
CH665262A5 (de) * 1984-06-22 1988-04-29 Bbc Brown Boveri & Cie Kippsegmentradiallager.
CH668811A5 (de) * 1984-07-19 1989-01-31 Glyco Metall Werke Hydrodynamisches gleitlager.
US4568204A (en) * 1984-09-04 1986-02-04 Kingsbury, Inc. Journal bearing

Also Published As

Publication number Publication date
US4815865A (en) 1989-03-28
DE3764931D1 (de) 1990-10-18
DE3617289A1 (de) 1987-11-26
WO1987007341A1 (fr) 1987-12-03
DE3617289C2 (fr) 1989-12-14
EP0269647A1 (fr) 1988-06-08
BR8707312A (pt) 1988-09-13

Similar Documents

Publication Publication Date Title
EP0269647B1 (fr) Palier a glissement radial hydrodynamique
DE2939945C2 (fr)
EP1644647B1 (fr) Palier lisse axial
EP2140114B1 (fr) Palier axial notamment pour un turbocompresseur
DE69721336T2 (de) Dynamisches gaslager mit folien
EP1148965B1 (fr) Lame de scie comportant des passages d'air allonges
DE4440868C2 (de) Temperatursensitive Ventilatorflüssigkeitsreibungskupplung
EP0230885A1 (fr) Turbosoufflante
EP0158242A2 (fr) Palier radial à contact lisse
DE10334880A1 (de) Anlaufscheibe für Planetengetriebe
DE2622204A1 (de) Formfolienlager
DE2356817B2 (de) Selbstdruckerzeugendes Radialgleitlager
EP0476395A2 (fr) Disposition des disques de support axial pour des satellites dans un porte-satellites
DE2838768B2 (de) Mehrflächengleitlager
DE3327119A1 (de) Luftlageranordnung fuer ein zahnaerztliches handstueck
DE4019699C2 (fr)
DE19804734A1 (de) Planetenscheibe
DE3905450C2 (de) Gleitlager
EP0287847B1 (fr) Outil de coupe
CH677009A5 (fr)
EP1266128A1 (fr) Structure de rigidification et de refroidissement d'une aube de turbine
DE3001061C2 (fr)
CH626959A5 (fr)
DE102016103396A1 (de) Bremsbelag einer Scheibenbremse und Bremsbelagsatz
DE8424844U1 (de) Flanschlager

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19880217

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE FR GB IT LI NL SE

17Q First examination report despatched

Effective date: 19890623

RBV Designated contracting states (corrected)

Designated state(s): AT BE CH DE FR GB IT LI SE

ITF It: translation for a ep patent filed

Owner name: DE DOMINICIS & MAYER S.R.L.

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE FR GB IT LI SE

REF Corresponds to:

Ref document number: 56507

Country of ref document: AT

Date of ref document: 19900915

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3764931

Country of ref document: DE

Date of ref document: 19901018

ET Fr: translation filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
ITTA It: last paid annual fee
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19940223

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19940321

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19940323

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 19940415

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19940425

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19940429

Year of fee payment: 8

EAL Se: european patent in force in sweden

Ref document number: 87902409.9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19950216

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Effective date: 19950428

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19950429

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19950430

Ref country code: CH

Effective date: 19950430

Ref country code: BE

Effective date: 19950430

BERE Be: lapsed

Owner name: BRAUNSCHWEIGER HUTTENWERK G.M.B.H.

Effective date: 19950430

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19951229

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19960103

EUG Se: european patent has lapsed

Ref document number: 87902409.9

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19960428

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19960428

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050428